Calculating machine



Aug. 28, 1945. w. E. mm

CALCULATING MACHINE Filed Sept. 30, 194

10 Sheets-Sheet 1 INVENTOR. WALTER E. MATH! A] IORNEYS Aug. 28, 1945. w. E; MATHI CALCULATING MACHINE Filed Sept. 30, 1940 10 SheBfMv-Sheel; 2

Aug. 28-, 1945.

W. E. MATHI CALCULATING MACHINE Filed Sept. 30, 1940 10 Sheets-Sheet 3 mmvma Vl ALTEP f. MATH/ ATTO EYS.

Aug.28, 1945. w. E. MATH. I 2,383,731

CALCULATING MACHINE Filed Sept. :s o, 1940 10 Sheets-Shed 4 2, 245 FIE- lE A mvszvron. WALTIP E MATH! ATTORNEYS Au 28, 1945. 3 w. E. MATHI 2,383,731

CALCULATING MACHINE Filed Sept. 30, 1940 10 SheetsSheet 5 ions 5 7 e 4 3v 2--/ FIE; 17 v Aug. 28, 1945. w. E. MATHI 2,383,731

CALCULATING MACHINE Filed Sept. so, 1940 10 Sheets-Sheet 7 A EYS.

Aug. 28, 1945. v w. E. MATHI CALCULATING MACHINE Filed Sept. 30. 1940 1o smut-fiat a :INVENTOR. WALTER E/WAT/fi 1 M w i w 2 A'ITORNEY5 Aug. 28, 1945. WL'E. MATHI CALCULATING MACHINE Filed Sept. 30, 1940 10 Sheets-Sheet-Q INVEN TOR. 14441.70? 6. MATH! ATTORNEYS Aug. 28, 1945.

W. E. MATHl CALCULATING MACHINE Filed Sept. 30, 1940 l0 Sheets-Sheet l0 :EIE- E15.

FIE 13E- INVENTOR. VMQLTE? F. MATH/ if ATTORNEYS Patented Aug. 28, 1945 UNITED STATES PATENT OFFICE 2,383,731 cawum'rme momma Walter E. Mathi, Oakland, -Calii'., assignor to Mar-chant Calculating Machine Company, a corporation of California Application September 30, 1940, Serial No. 359,054

3 Claims.

lected values may be entered and the selection and actuating mechanism respectively by means of which desired values are set up, in order that the selected values may be introduced into different denominational orders of the accumulator register as may be necessary in operations of division or multiple-factor multiplication.

It has therefore been customary either to arrange the selection and actuating mechanism to be movable while keeping the accumulator register stationary or, as was more frequently the case, to provide for transverse movement of the accumulator register relative to a stationary selection and actuating mechanism,

Due to the relative movability of two such large units of a calculating machine, however, such machines occupied excessively wide desk space. Also, the shifting operation of the accumulator register relative to the selection mechanism disturbed the symmetrical appearance of the machine, and was usually accompanied by undesirable noise.

It is an object of the present invention to provide a calculating machine of great compactness and well-balanced symmetrical appearance which undergoes no changes in its external shape during operation, and which has yet all the advantages of denominational displacement between the selection mechanism and the accumulator register.

It is another object of the present invention to furnish a calculating machine in which the ordinal position of the values set up in the factorselecting mechanism may be varied relative to the accumulator register into which they are entered, while both the selection mechanism and the accumulator register of the machine are kept sta-..

tion to provide an arrangement for a smooth and unobstructed transmission of the digital motion of the actuator as determined by the selection mechanism of a calculating machine to a movable transmission mechanism and from there tothe accumulator register, no matter what the ordinal position of said transmission mechanism relative to said selection mechanism and to said accumulator register may be.

It is another specific object of the present invention to provide a calculating machine of the type referred to, in which lateral displacement of the movable transmission mechanism, relative to the stationary selection and actuating mechanism and to the stationary accumulator register may be effected without any risk of obstruction, such as may occur by unavoidable variations in alignment between the gears of the transmission mechanism and the accumulator register.

The manner in which the above and other objects of the invention are accomplished will be readily understood from the following specification when read iii conJunction with the accompanying drawings, wherein .Fig. 1 is a perspective view of a calculating machine embodying the present invention;

Fig. 2 is a vertical longitudinal section illustratin the keyboard for selecting a value, the actuator mechanism, the accumulator mechanism, and the counter mechanism;

, Fig. 3 is a section taken along the line 3-3 of Fig. 2, showing the typical construction and mounting of a key;

Fig. 4 is a perspective view of a keyboard check dial;

Fig. 5 iS a section taken substantially along the line 55 of Fig. 2, illustrating the shiftable transmission and the means for driving the same;

Fig. 6 is a section taken along the line H of Fig. 2, illustrating details of the shiftable transmission;

Fig. '7 is a section taken along the line of Fig. 5, showing the gear connections for certain of the transmission shafts;

Fig. 8 is an enlarged partial section taken substantially along the line 88 of Fig. 2, illustrating the accumulatin and tens-transfer mechanisms, with the tens-transfer mechanism partly through its cycle of operation;

Fig. 9 is a transverse section taken along the line 9-9 of Fig. 8, illustrating one of the transfer units;

Fig. 10 is a section through the same unit, taken along the line i0i0 of Fig. 8;

Fig. 11 is a transverse section taken along the line ll-ll of Fig. 8, illustrating one of the differentially driven accumulator dials and the pawling means therefor;

Fig. 12 is a section taken along the line 12-42 of Fig. 8, illustrating a transfer unit different from that shown in Figs. 9 and 10;

Fig. 13 is a full size vertical section through the accumulating and counter registers, illustrating the transfer levers and transfer units associated therewith.

Fig. 14 is a vertical section through the accumulator and counter mechanisms, illustrating the clearing mechanism;

Fig. 15 is a section takenalong the line l5-l5 of Fig. 18, illustrating the means operated by the clearance drive for releasing the dial pawls;

Fig. 16 is a section taken along the line lS-Hi of Fig. 26, illustrating the means operated during tens-transfer operation for releasing the dial pawls;

Fig. 17 is a schematic development of the tenstransfer assembly, illustrating th cross-over staggered relation of the transfer teeth;

Fig. 18 is a developed sectional view taken along the right-hand side of the machine, looking down, illustratingthe driving connection for the actuator and clearing mechanisms;

Fig. 19 is a perspective view of one of the clutch members forming part of the drive of the clearing mechanism for one of the registers;

Figs. 20 and 21 are front and edge views, respectively, of the driving member of one of the unidirectional clearance clutches;

Fig. 22 is a perspective view of another clutch member forming part of the drive of the clearing mechanism for one of the registers:

Fig. 23 is .a section taken substantially along the line 23-43 of Fig. 18;

Fig. 24 is a section taken through the forward part of the machine. illustrating the manual drive connection for the shift mechanism;

Fig. 25 is a section taken along the line 25-45 of Fig. 24;

Fig. 26 is a developed section taken along the left side of the machine, illustrating the drive for the actuator, accumulator, transfer mechanism, and counter mechanism;

Fig. 26A is a section through one of the reversible drive clutches;

Fig. 27 is a transverse section taken along the line 21-21 of F18. 26; v

Fig. 28 is a section taken along the line 2823 of Fig. 26, illustrating the lost motion connection in the drive for the accumulator mechanism;

Fig. 29 is a section taken along the line 23-43 ofFig. 28;

Figs. 30 and 31 are sections taken through one of the reversible drive clutches;

Fig. 32 is a longitudinal, vertical section takensubstantially along the line 32-32 of Fig, 26, illustrating the multiplier control section and the drive for the accumulator transfer assembly and counter mechanism;

Fig. 33 is a section taken substantialiyalong the lines 33-43 of Fig. 32;

Fig. 34 is a detail section taken along the line 34-34 of Fig. 32.; Fig. 35 is a section taken through the add and clear bar mechanism for releasing depressed keys;

Fig. 36 is a detail section taken along the line "-3. ofFlg. 35;

Fig. 3'? is a section show ng the counter reverse control;

Fig. 38 is a section illustrating the keyboard lock and means for operating the same;

The machine of the present invention is of the key-set type in which means are provided for first setting up one factor of a calculation on a keyboard and subsequently operating the machine under power, preferably derived from a crank, in a manner indicated by the character and amount of another factor of the calculation.

Key-set mechanism In a machine designed for calculation in the decimal system, the keys are preferably arranged, as shown in Fig. l, in a series of banks of ten keys each, the number of banks provided in the machine depending upon the magnitude of the factor with which the machine is designed to deal.

As indicated, each key bank or section comprises a row of value keys 40, the key stems 43 (Figs. 2 and 3) of which are slidably mounted in a channel-shaped key frame 4|, and normally maintained in raised position by suitable coil springs 42. The key stems 43 are assembled into the channel frame 4i from the top, the slots in the upper flange of the channel frame being of sufficient width to pass camming projections 44 formed on the key stems 43. After insertion of the key stems, a retaining strip 45 is secured in place by screws 46, thus preventing withdrawal of the keys.

Each key section is mounted in the machine between a cross channel member 41 and a cross bar 48, forming part of the stationary framework of the machine. The rear ends of the channel members 4| are provided with slots 49 which are fitted over the upper flange of the channel member 41, enabling lengthwise adjustment of the key sections. After assembly of the various key sections, they are aligned with each other by means of set screws 50 threaded in the cross bar 48 and abutting each channel 4|. The key sections are then secured in place by screws 5|. After assembly of the key sections, decimal markers 52, having finger pieces 53 formed on the forward ends thereof, are journaled between adjacent key banks. As is well known, one side of each of these markers is colored to correspond with the coloring of the top of channels 4i, while its other side is colored to contrast therewith, so that by turning the selected markers, the keyboard may be set of! in any desired manner.

Disposed beneath the camming projections 44 of the key stems 43 in each bank of keys is a differentially settable bar 54 having elongated slots 55 formed therein and slidable along bearing screws ll secured to the side of the channel 4|. This bar I4 is provided with a series of camming surfaces, one located adjacent each key stem 43. Each of these camming surfaces, as

at N and I2, is arranged at an angle different from that of any other of the camming surfaces,

whereby depression of any one of the value keys 4. will cam the bar 54 rearward an amount different from that produced by depression of any other of the value keys. As illustrated in Fig. 2, each bar 84 is urged forwardly by a tension spring I extending between a lug formed on the bar 54 and a lug formed on the channel 4|.

At the rearward end of each bar 54 is a verticoll! extending slot I in which rides a pin 02 secured to the lower end of a check dial lever. This lever is pivoted on a cross rod 63 extending the width of the machine and supported by 14 thechannclmembersfl. Anarcuatecheckdial 64 (Fig. i) is formed on the upper end of each check dial lever. Arranged on the upper surface of each dial 64 is a series of numerals 65. These numerals are so connected as to form a con-' densed series of numbers from zero" to nine.

The camming surfaces 59, 59, et cetera, formed on each differentially settable bar 59 are so arranged as to cause the associated dial 64 to exhibit a numeral representing the value of the key depressed. This numeral will be visible through an opening 66 formed in a cover plate 61 which/ forms part of the stationary framework of the machine. For example, on depression of the numberv "3 key the check dial 64 will be moved to a position wherein the section extending between the dotted lines 68 of Fig. 4 will be visible through the opening 66.

The manner in which the check dials 64 are mounted on the key section frame so as to form a unitary key section assembly is particularly advantageous from the production point of view, in that the variables between the'value keys 40 and the check dials 64 can be far better controlled in this way than if the check dials 64 were constructed to form a separate unit mounted on the machine frame. Among other advantages. proper lineup of the check dials with respect to the sight openings 66 (Fig. 2) is greatly facilitated.

All of the key stems 93 in each bank, except the front one, are of the same length. Each has a cam projection III which, on depression of the key, pushes a slotted key-locking slide 1!, slidably supported on the lower side of the channel ll, to the right, as viewed in Fig. 2, thereby releasing any other latched-down key in-the same section. Upon full downward depression of any value key stem, this slide. urged forward by a compression spring 12, snaps back into its initial position and by overlying the upper edge of the projection 70, latches the depressed key.

The leftmost key (Fig. 2) in each section, is the zero or clear key, and is provided for the sole purpose of releasingany latched-down key in the same section or bank. The cam projection of this key is identical with that of the other keys of the section, but latching down of the .zero key is prevented by the provision, on the locking slide H. of a lip 13, the lower edge of which extends below the lowermost position assumed by the top of the projection 19. Hence, while the slide is moved to the right upon depression of this key for the purpose of unlatching any latched-down key, the lip II prevents it from returning leftward during the depression of the key, and latching of the key cannot be effected.

Besides the individualzero or clear key for each key bank described above, a main clear key 16 (Figs. 1 and 35) is provided, which, upon depression thereof, will release every depressed key on the entire keyboard. This key is slidably mounted for vertical movement on a pair of pins 19 and TI suitably secured to the machine frame. Key II is normally held in a raised position by a tension spring 19 and has a lug 19 formed on the lower end thereof which, upon depression of the key, engages and rocks a bellcrank 69, pivoted on a pin 8|, against the action of a tension spring 92. The upper end of bellcrank 69 is connected by a link 99 to a clear gate 69 extending the entire width of the keyboard and pivoted on studs 9! supported by the side frames of the machine. The upper portion of the gate 94 extends directly in front of each of the locking slides ll (Fig. 2).

Thus, whenever the clear key 16 is depressed, the gate 64 will be rocked clockwise to release any latched-down key. Under some conditions, the keyboard is cleared automatically by rocking this gate, as will be described hereinafter.

' As illustrated in Figs. 2 and 3, each of the key stems of the value keys 9 is slotted at the lower end, to form two spaced legs 86, which straddle the reduced portion 98 of a gear member 99 slidable along a, square shaft 9!, and having formed thereon a spur gear 99. Each shaft 9| is aligned directl below its associated key section, and is journaled in bearings 92 and 99 provided in the cross channel member 41, and in a supporting plate 94, respectively.

The legs 66 of each key stem are bent slightlyforward, so that upon depression of a value key into its latched position, as indicated by the dotted lines the legs 96 engage the rear edges of the reduced portion 69 on the associated gear member 89, and move the member rearwardly along the shaft 9! until the gear 99 is positioned in meshing relation with an adjacent actuator gear 96 secured on a second square shaft situated directly below the shaft 9| and journaled in bearings 91 and 99 also provided in the channel member 41 and supporting-plate 99, respectively.

Actuator mechanism The actuating mechanism of the present invention embodies the well-known Thomas type prin-- section have graduated numbers of teeth, the gear 96 adjacent the #1 value key having one tooth, the gear adjacent the #2 key having two teeth, et cetera, up to the last or rear-most gear 96 which has nine teeth. In contrast to this arrangement, the selector gears 90 all have the same number of teeth which, in this case, is nine. Thus, upon depresssion of a value key in any bank and subsequent rotation of the shaft 95 for one revolution in a manner described hereinafter, a rotation will be imparted to the shaft 9|, the amount of which depends upon the value key depressed. It should be noted that the various gears 96 are so arranged on the shafts 95 that their teeth are symmetrically distributed about a, vertical plane passing through and along-the axis of the shafts 95 when the machine is in its illustrated full cycle position.

With the actuators disposed directly beneath the individual key sections, as shown in Figs. 2 and 3, it is possible to dispense with the usual linkage connections between the various key sections and their associatedactuators. Linkage connections of this type generally require a variable stroke for the diflerent value keys depressed. and this causes an uneven key touch which is particularly noticeable between lowest and highest value selectlons. Furthermore, such linkage connections require critical adjustment. The present invention overcomes this difliculty entire'y. in that all the gears 99 are shifted the same amount to bring them into engagement with their associated actuator gears 96, and thus an absolutely even key touchis obtained over the entire keyboard.

The various actuator shafts 95 have gears 99 on their rearmost ends, which gears mesh with similar gears I secured on a main actuator shaft III I the latter extending across the machine and being journaled in bearings H2 and "2' (Fig. mounted on brackets extending from the channel member 41.

Actuator transmission mechanism The present invention provides an actuator transmission that is shiftable relative to the registering mechanism, thereby enabling the registering mechanism to be stationarily supported in the machine, instead of being carried by a carriage which is shiftable relative to the machine. Since this shiftable transmission may be situated well within the confines of the machine (instead of on the exterior thereof as is the case with machines wherein the registers are supported by shiftable carriages) the noise incident to such shifting operations may be minimized, and the registering mechanism may be arranged to present a symmetrical, well balanced appearance. I

The shiftable transmission, or carriage. is generally indicated at I03 (Figs. 2, 5 and 6) and is operated by the various actuators, in a manner hereinafter described, to transmit actuation to different denominational orders of the actuator register.

The transmission Illl'is supported for shifting movement laterally of the machine by a worm shaft Ill, and by a plurality of drive shafts Ill equi-spaced from each other and arranged equidistant from the worm shaft III, as shown in Fig. '7. The worm shaft IN is supported at opposite ends thereof in bearing sleeves I" and I" secured in end plate assemblies Ill and I", respectively. Each of these end plate assemblies comprises a pair of plates III and III held apart by suitable spacers as at I02. Spacer rings III are fitted over the sleeves Ill and I" intermediate the plates III and III to also aid in bolding the plates in their correct spaced-apart positions. The entire shiftable transmission I, as

well as the end plate assemblies Ill and III, are supported for a slight vertical movement, by arms III and II: (Fig. 5) rockably mounted at their rearmost ends on frame studs I which are secured to end plates III. Each of the arms H2 and I I3 has an enlarged forward annular portion in which the respective sleeves IO. and III are secured, a sleeve I" being shown in section in Fig. 6.

In order to raise and lower the shift-able transmission I03, a rotatable cam shaft III is provided, extending across the machine and ako journaled in the end plates III. Two pairs of complementary cams III and III (Figs. 2, 5 and 23) are mounted on the cam shaft III. one pair aratedto allow the transmission III to be shifted sideways. At the beginning of a machine operation the cam II'I immediately rocks the cam follower IIl, and consequently the arms H2 and I II, to bring the transmission gears I22 into close mesh with gears I21, thereby insuring quiet and accurate operation of the machine during the succeeding actuation.

The different drive shafts I" are connected to different ones of the intermittently operated shafts SI by flexible shafting and gearing. The number four" shaft fl (Fig. 5), counting from the right side of the machine, has secured thereto by means of a sleeve III, a flexible shaft I24, which is secured at the other end in a socket formed in a gear I25 having hubs thereof iournaled in the two plates III and III of the end plate assembly I". The flexible shafts may be held in position by any well known means such as clamps or anchor bearings, not shown, so as to prevent interference of the shafts with the slidable transmission I02, and also to prevent whip of the shafts when the direction of rotation thereof is reversed. Gear I25 (Figs. 5 and '7) meshes with a similar gear I28, having hubs Journaled in bearings formed in the plates III and III, and having secured thereto one of the shafts III; the other end of this shaft is secured in a sleeve I21 Journaled in bearings formed in the end plate assembly I". The various other shafts ll are similarly connected to their associated drive shafts I". However, the rightmost four shafts SI, representing the keyboard orders one to "four," are connected to gears located on the end plate assembly III, while the leftmost four shafts lI, representing the keyboard orders "five" to "eight," are connected to gears located on the left endplate assembly I. Furthermore, to enable close spacing ofrthe shafts III, certain pairs of the gears (as I25 and I2) are positioned between the plates III and I II of the endplate assembly I" or I", while other pairs of gears. for example gears I28 and I2! (Fig. '7) are located outside of the plates III.

The shiftable transmission Il 2 comprises a pair of end plates III and I22 between which are spaced a plurality of plates Ill. These various plates are mounted on and secured to a sleeve Ill (Hg. 6) which is threaded at its righthand end to fit the threads of the worm shaft I.

- The various plates III, I32 and III are held in at either end thereof, and each pair is'snsased by cam followers III and I2, depending from each of the arms '2 and III. The cam shaft Iii is driven in a manner described hereinafter, and the timing is such that, when the machine is in full cycle position, a lobe IN on each of the cams II! engages a roller l2. on the cam follower I2. and thereby moves the arms H2 and H2. as well as the slidable transmissicn Ill, into a slightly dipped position as shown in Fla. 2. 1h

' this position of the transmission I". transmission gears I22, forming a part thereof, are out of close mesh with gears I22 forming part ofthe accumulator register gear train. However. the gears I22 and I22 in each order of the shiftable transmission In are not completely out of mesh with each other; they are merely simicienfl! IP- spaced relation with each other by spacer combs I (Fig. 2) interlocking with slots In the various plates and held in looking position by rods I31. Each end plate has a plurality of bushings Ill Journaled therein and registering with the drive shafts Ill. The bushings I2! have square openings therein adapted to fit the square shafts Ill. so as to guide the trananission along the latter.

Inbrposed between the various plates Ill, I82 and I2! and iournaled on the sleeve IN is aplurality of main transmission gears I22. As described hereinbefore, these gears mesh with the gears I2! driving the various accumulator "8 ter units, and are em -spaced from each other a distance equal to the spacing between the gears I23. Thus, each of the gears I22 can be directly aligned with one of the gears I28.

Bplined to each drive shaft Ill and located intermediatetwo ofthespacerplates Ill isa gear Ill meshing with an associated transmission gear I21. These gears I are so located that each will rotatethe transmissiongear I22 inthatorderof the Ill tothe order ontheheyboardinwhichmch rotationwasinstituted. For example, the number four" actuator gear I 22, counting from the right side of the transmission I03, meshes with a gear I40 splined to the shaft I05 that is driven (through gears I25 and I26 and flexible shaft I24) from the shaft 9I associated with the number four key bank.

In order to preventinadvertent rotation of the gears I22 when they are not being actuated, as well as to insure against interference of the teeth of those gears with the teeth of gears I23 during a shift of the transmission I03 from one position to another, means are provided for pawling the various gears I22. To this end, a helical tension spring I45 (Figs. 2, 5 and 6) is passed through aligned openings inthe various plates I33 and is secured in similar aligned openings in the end plates I3I and I32. When the gears I22 are at rest, the. spring I45 lies between adjacent teeth thereon, as shown in Fig. 2, and therefore yieldably restrains the gears from rotation.

Extending upwardly from the two end plates I3I and I32 of the shiftable transmission I03 are a pair of brackets I46 (Fig. 2), An indicator plate I41 (Figs. 1 and 2) is secured to the brackets I46 by screws I48 and extends through a slot I49 to apprise the operator of the lateral position of the actuator transmission I03 at all times. The plate I41 has a series of numerals thereon corresponding to the orders of the keyboard and spaced apart a distance corresponding to the spacing of the transmission gears I22 so as to indicate the orders of the accumulator register (visible through openings I50) into which values setup in the various correspondingly numbered orders of the'keyboard will be entered.

To readily correlate a key bank with the corresponding accumulator dial into or from which a value is to be added or subtracted, with the shiftable transmission I03 in a particular position, the various sections of the key columns are colored differently, and the columnar numbers on the indicator plate I41 are each identified with the same color as the corresponding key column. For example, if the keys 40in the two right-most banks, as viewed in Fig. 1, are colored green, the next three adjacent banks colored yellow, and the three next banks colored green, then the two lowest numbers on the indicator plate I41, representing the two right-most key columns, would be disposed on a green field, the next three numbers representing the yellow keys would be disposed on a yellow field, and the next three and highest numbers would be disposed on a green field. Thus, using the colors to guide him, the operator can at a glance, correlate the key banks and the corresponding accumulator dials, visible at I50, into or from which values set up in particperiphery of the disc I60, by a tension spring I53.

Gearing, to be presently described, connects the shift handle I52 to the worm shaft I04 (Fig. 5) for the purpose of shifting the transmission I03 from one position to another, and is so arranged that one of the indentations on the disc I50 will beengaged and centralizedby the roller IGI whenever the transmission I03 is in oneof its different positions of rest.

The shaft I59 (Figs. 2 and 23) is journaled at its rearmost end in a bearing formed in a bearing bracket I65 which is suitably secured by screws I66 to a cross piece forming part of the machine base I61. Secured to the shaft I59 is a spiral gear I66, which meshes with similar spiral gear I69 to a cross shaft I10. Shaft I is joumaled at one end in a bearing formed in the bearing bracket I55 and at the other end in a bearing formed inthe supporting plate II5. It has secured thereon (Figs. 5 and 23) a spur gear I12 meshing with a second spur gear I13 journaled on a bearing stud I14 extending from the supporting plate II5. Gear I13 drives a pinion I15 secured to the worm shaft I04, as shown in Fig. 6, andextends in close mesh with this pinion when thetransmission I03 is in its dipped position. As the sleeve I34 is moved along the worm I04, due to rotation of the worm,

. relative to the transmission by the plates I33) ular key columns would be entered or subtracted with the shiftable transmission I03 in a certain position.

Shift mechanism As stated hereinbeforathe transmission I03 is shiftable transversely of the machine to enable factors set up in the various banks of the keyboard to be added to or substracted from different orders of the accumulator register.

To provide for-this function, a manually operable shift handle I52 (Figs. 1 and 24) is provided at the front end of the machine. Handle I52 is secured to a short shaft I53 which is journaled in a bearing sleeve I54 mounted on a supporting plate I55 and is also iour'naled in a. second supporting plate I55. A spur gear I51 (Figs, 24 and 25) is secured to the shaft I53 and meshes with various plates I11.

slide along their respective drive shafts I05.

Accumulator mechanism In contrast to the transversely shiftable accumulator or product registers usually provided on calculating machines of this character, the machine of the present invention employs a stationary accumulator. Thus, the overall width of the machine is maintained at a minimum, and the noise incident to shiftable accumulator register carriages may be'dispensed with. A further advantage of this type of stationary accumulator is that distraction of the operator causedby the bodily shifting of the accumulator dials is eliminated.

As was stated heretofore, the accumulator register comprises a series of numeral dials representing successively higher denominational orders, which dials are visible through openings I50 (Figs. 1 and. 2) in the cover plate 61 of the machine, and which are driven through individual gear trains, including the gears I23.

A. plurality of brace plates I11 (Figs. 2, 8 and 13), are equl-spaced along the inside of the cover plate 51 and supported at their lower extremity is a cross rod I15 extending the width of the machine. The various gears I23 are rotatably mounted'on this rod I16 and mesh with gears I19 secured to the hubs of sun gears I60 journaled on a cross rod III, also supported by the Each sun gear I meshes with diametrically opposed planet gears I92 (Figs. 8 and 11) journaled on pins I03 secured to a disc I35 freely mounted on the hub of the dials, to positively lock the disc I88 from rota-' tion. A leaf spring H88 is secured to the shaft I88 by a small screw II8I and engages the under surface of pin H88 to yieldably urge the pawl I81 into engagement with the disc I88 when the arm H88 is removed from contact with the pin H88. Under certain conditions, during transfer of tens, and during clearance of the dials, as will be explained hereinafter, the shaft I88 will be rocked clockwise a limited amount, removing the arm H88 from the pin II88 but enabling the spring II88 to still yieldably hold the pawl I81 against the disc I88. With the parts so arranged, the disc I88 may be rotated but the pawl I81 will effect centralizing of the same when it comes to rest, and will also tend to prevent overthrow due to momentum of the dial assembly.

Each of the planet gears I82 has a second set of gears I88 carried thereby and meshing with a second sun gear I88 also freely rotatable on the shaft I8I. Secured to the hub of the sun gear I88 are, in turn, a transfer lever knock-out cam I8I, a mutilated clearing gear I82, a transfer gear I88, a dial shell I88, and a supporting disc I88 for the shell I88. To secure the various elements on the sun gear I88 together, a pin I81 may be passed through the gears I82 and I88, as well as through the dial shell I88 and disc I85. The periphery of the dial shell is sufflciently wide to accommodate equi-spaced numeral digits ranging from "0" to "9."

The gearing interconnecting the various shafts 8i (Fig. 2) with the various dial shells I88 is so arranged that, upon each one-ninth of a revolu tion of a shaft 8i, the respective dial I88 arranged to be driven thereby will be advanced one-tenth of a revolution or from one numeral to the next. For example, if the number "five numeral key 88 of a particular key section is depressed, one revolution of the associated actuator shaft 88 causes the respective gear 88 to impart after described and which carries a plurality of transfer units generally indicated at 28 I, 282, 288, et cetera, one for each accumulator dial assembly. This shaft 288 remains stationary during digitation, but during the latter part of the cycle it is rotated through one complete revolution, and during this rotation the various transfer units thereon will cause a tens-transfer to any accumulator dial if the next lower dial has moved from 9" to "0 in an additive direction, or from 0" to "9" in a subtractive direction.

Referring to Figs. 8 and 12, the shaft 288 is square and each of the transfer units 28I, etc, with the exception of those to the left of a unit 28I (Fig. 17), comprises a sleeve 28I splined to the shaft 288. Secured to the sleeve I is a guide 281 in the form of a stamping having a hub 288 formed thereon which is firmly pressed on the sleeve 28I. Each guide 281 except the one attached to the unit 28I (which will hereinafter be termed the common transfer unit") and all those to the left thereof, has two radially extending slots formed therein which guide a pair of transfer teeth or keys 2" for endwise sliding movement longitudinally of the shaft 288. Each tooth 2I8 is also slidable in a radial slot formed in a guide plate 288 secured on the lefthand end of the sleeve I. A compression spring 2 is interposed between the plate 288 and a shoulder 288 formed on each tooth 2" to normally press the teeth to the right, as viewed in Fig. 8.

It will be noted that each tooth m has an mclined edge 2I2 formed thereon which, when the tooth is moved to the left against the action of the spring 2| I, moves into meshing relation with a gear 2I8 Journaled on a shaft 2 which is supported by the various plates I11 and which extends across the machine. The gears 2I8 mesh with the heretofore mentioned tens-transfer gears five-ninths of a revolution to the corresponding sear 88 to advance the dial shell I88 driven thereby through five numerals.

' A positively operated gate (not shown) or individual spring pressed pawls (not shown) are preferably provided to lock the gears I18 against inadvertent rotation after having been advanced during digitation. Since such means is old and well known in the art as indicated in the United States patent to Lerch, No. 1,927,289 issued September 19, 1933, it is not necessary to show the details of it herein.

Tens-transfer and 13).

I88 secured to the respective dials I88.

Each transfer tooth III has an inclined edge 2I8 opposite to edge 2I2 and this edge 2" is normally in the path of a rounded tip 2" formed on the lower end of a transfer lever 2" (Figs. 8 Said lever 2" is pivoted on a cross rod 228 supported by the various plates I11, and has an elongated slot 2I8 formed therein and extending over a spacer sleeve 2I8' on the shaft 2 whereby the lever maybe swung in a limited are about the rod 228. A hair pin spring 22I is secured to a pin 222 extending-from the lever 2" adjacent the offset tip 2I8' thereof and embraces the sleeve 2l8' on the shaft 2 so as to yieldablyhold the lever 2" in either of two extreme end positions.

In full cycle position of the machine. or whenever no transitional carry is to be effected, each transfer lever 2I8 is maintained in the position illustrated in Fig. 13, with a forwardly extending point 228 thereon closely adjacent the periphery of the heretofore mentioned knock-out com "I secured to the dial shell I88. As the respective dial is rotated from 0" to "8 in one direction or from 9" to "0" in an opposite direction a lobe 228 formed on the knock-out cam I8I engages the point 228 of the lever 2 and thus moves this lever counterclockwise to pocitionih rounded tip 2" in the path of one of the transfer teeth 2i8 ofthe transfer unit for the next higher order dial assembly. Upon subsequent rotation of the transfer shaft 288 a transfer tooth III will engage the extended tip III and, due to the inclined surface 2 thereof, as well as to the rounded portion of the tip III, the tooth 2" will be moved to the left into meshing engagea,sas,7s1 I ment with the respective gear 3. Continued rotation of the shaft 200 will cause the carry tooth 2|!) (now in mesh with the associated sear 2l3) to advance the gear H3, and consequently the respective dial shell I90 one increment, or from one numeral to the next.

It is to be noted that, due to the inclined surfaces H2 and MB of the various transfer teeth 2 I0, as well as to the rounded contour of the tips 215? of the transfer levers M5 and the curved contours of the teeth of the gears 2l3, the teeth 210 need not be entirely meshed or engaged with the gears 2|3 before beginning their advancing movement.

Each of the transfer units 2!, etc. to the I right of the common transfer unit 20I (as viewed in Fig. 17) has a transfer lever return cam 223 securely mounted on an annular member 205 (Fig. 8) which, in turn is suitably secured on its respective sleeve 23!. Each of the cams has a lobe capable of engaging the pin 222 on the associated transfer lever M5, to return this lever to its original position illustrated in Fig. 13, after a transfer has occurred in the respective order, re-

gardless of which direction the shaft 200 is rotated.

The construction of the transfer units 202, 203, etc. to the left of the common transfer unit 20! is shown in Figs. 8, 9, and 10. This construction is somewhat similar'to that of the units to the right of unit 20l'; however, only one transfer tooth 210 is provided for each of these latter units. Furthermore each guide 231' is mounted on an annular sleeve 230 which is freely mounted for rotation on a second sleeve 204, splined to the shaft 200. A pin 232 extends through the hub 203' of each guide 201 and throughthe annular sleeve 230 and rides in a slot 233 formed in the inner sleeve 200. The lengths of the slots 233 inthe various units to the left of the unit 20! (Fig. 1'7) vary froma minimum in the transfer unit immediately to the left of unit 20l' to a maximum in the transfer unit at the extreme left of the transfer assembly.

Due to the lost motion of the pins 232 in the respective slots 233, those transfer teeth 2 to the left of the unit 21" can lag behind a certain amount, upon rotation of the shaft 200.

Considering the developed view of Fig. 17, ad-

ditive operation of the machine will effect movement of the entire transfer assembly mounted on the transfer shaft 200 in thedirection of the arrow A, while subtractive operation of the machine will effect movement of the transfer assembly in an opposite direction or in the direction of the arrow S. v

Now the various teeth 2 II! in the transfer units to the right of the tooth of unit 20] are arranged in two helical rows diverging from the single tooth of the unit 20! which tooth is common to both rows. Also, the hereinbefore mentioned slots 233 (Figs. 8 and 10) in the various transfer units to the left of the transfer unit 201 are of such lengths that, as the shaft 200 is rotated to move the transfer assembly in the direction of the arrow A, the teeth 2! of these latter mentioned transfer units will, by virtue of a drag means to be described, assume the positions illustrated in full lines in Fig. 1'7, wherein they form a continuation of one of the two mentioned lustrated in dot-and-dash lines in Fig. 17 wherein they form a continuation of the other of the two mentioned helical rows of transfer teeth.

As indicated diagrammatically in Fig. 17, all of the floating transfer units 202, 203, etc. tothe left of the rigidly mounted common transfer unit 20l, as well as this unit 2M, are provided with floating transfer lever return cams 225'. Each of these cams 225' is capable of being rocked from one side of its adjacent transfer tooth 2|0 to the other a limited amount. This provision enables the cams 225' to return the respective transfer levers 2|! (Figs. '8 and 13) to their original positions (provided they have been moved therefrom by cams 13!) only after a transfer has taken place and regardless of the direction of movement of the transfer assembly. To effect this lost motion connection between the floating cams 223 and their respectivetransfer units, each floating cam is rotatably mounted on an annular member 205' rigidly secured to the associated sleeve 230 or 23! in the case of the common transfer unit 20l'. A bearing washer 301 is interposed between each member 205 and a collar 603 riveted to the associated supporting sleeve.

As shown in Figs. 8 and 9, each of the floating cams 225' has an extended notch 226 formed therein, into which extends a lug 221 formed on the adjacent member 205'. The notch 226 is so arranged that the return .cam 225 may be moved to one side or the other of its respective transfer tooth 2l0.

Referring to Figs. 8 and 9, a frictional drag assembly, generally indicated at 600, is provided to cause each floating transfer cam 225' to remain stationary after the shaft 200 starts to rotate, until the lug 221 abuts the trailing end of notch 223, and until the pin 232 (Fig. 10} abuts the trailing end of slot 233, if such has not previously occurred. Therefore, this drag assembly insures that both the floating transfer units and the floating cams 225' will assume their correct positions, as shown in full lines in Fig. 17, when the machine operates in an additive direction to move the transfer assembly in the direction of the arrow A, and it also insures that these elements will assume their illustrated dot-and-dash line positions when the transfer assembly is.

moved in the direction of the arrow S.

The assembly 600 includes an angle bar 6M (Figs. 2, 8 and 9) extending between the side frames of the machine and supported thereby. This bar has a series of lugs 802 extending therefrom, each aligned with one of the floating cams 223'. A pair ofleaf springs 803 are secured to each lug 002 by a rivet 003, and they extend into frictional engagement with the opposite sides of the aligned floating cam 225' to effect a drag on this cam.

Due to the special, cross-over, staggered reiation of the various transfer teeth 2H1 (Fig; 17 the tens-transfer portion of the operating cycle may be reduced, enabling a slower speed of operation of the driving elements during digitation as well as rendering it possible to reduce the over-ail! diameter of the transfer assembly mounted on the shaft 200. Both of these factors tend toward an extremely quiet construction.

The operation of the carry mechanism is as follows: Assume, for example, that an unbroken series of nines appears on the various accumulatorjdials I and that the number "4" is to be added into the right-hand or number 1" order dial. Now as the accumulator dial in the number 1 order is rotated from 9" through to "3 during digitation, the cam In (Figs. 8

. and 13) in the number "1 order will rock its associated transfer lever 2|! into transferring position as has been described hereinbefore. Therefore, upon subsequent rotation of the transfer shaft 2" during the latter part of the current cycle to effect transfer, the number 1 order transfer lever 2|! will be impinged by its associated transfer tooth 2", indicated as the lower tooth m in the number 1" column of Fig. 17. lfhe lower tooth 2l0 will become active to effect a transfer because of the fact that the transfer assembly is moved in the direction of the arrow A during additive operations and therefore the lower tooth 2") will strike the associated lever 2|! first.

Thus the lowermost tooth 2I0 of the number 1 column (Fig. 17) will be shifted leftward to effect rotation of the number 2 order accumulator dial from 9 to 0 in the manner described hereinbefore in connection with Fig. 8. Since this action causes the knock-out cam MI in the number 2 order to throw its associated transfer lever 2|! into transferring position, the lowermost tooth 2" in the associated order (number "2 column of Fig. 17) will now strike this lever H5 and consequently be moved to the left to cause a partial rotation of the number 3" order accumulator dial from "9 to 0.

Due to the fact that, as before stated, the various teeth 2 l 0 to the left of the common transfer unit 2M will be arranged as shown in the full lines of Fig. 17 during additive operations. the above mentioned carry operation will continue sequentially from order to order to the left until the leftmost accumulator dial is reached, providing the series of nines originally extended completely .across the accumulator. Thus, instead of a series of nines a series of zeros will appear on the dials I94.

When the transfer assembly has moved through one-half of a revolution the fixed, transfer lever, return cams 225 on those orders to-the right of the common transfer unit 2lil' will strike their associated transfer levers 2 I! to remove thesame from transferring position before'the upper helical series of teeth 2 ll, illustrated in Fig. 1'7, pass the camming edges of levers 2i5. Also since the floating, transfer lever, return cams 22! on those units to the left of and including the common transfer unit are allowed to lag behind their respective teeth 2N, these cams 225' will operate to return their respective transfer levers from transferring position shortly after the respective teeth 2") have effected a carry movement.

Counter mechanism A counter mechanism compris ng a series of dials 2 (Fig. 26), visible through openings 2" (Figs. 1 and 2) in the cover plate '1, is provided so that the number of operations performed in addition or subtraction may be registered, the mechanism also serving as a multiplier register in multiplication operations, and a quotient register in division operations.

Each counter dial 2!! (Figs. 2 and 28) has numeral digits, ranging from "0" to 9," provided in equi-spaced relation around its periphery and is secured to a flanged hub 2M freely mounted on across rod 2" supported by the various brace plates I11 and extending across the machine. Secured tc the hub 234, as by a pin 2", are a gear 222 and a mutilated clearance gear 253. Gear 252 meshes with a gear 2" freely mounted on a second cross rod 233 also supported by the brace plates Ill. One of the counter dials 25i, depending upon the position of the shiftable transmission )3, is adapted to be driven one increment for each complete machine cycle by a counting finger 253 which is adapted to engage and advance the gear 231 aligned therewith an increment of one tooth. The rearmost portion of the counter finger 23! is Journaled on an eccentric portion 260 of a sleeve 2'2 splined to a'square drive shaft 28l. Shaft 26! is rotated one complete revolution for each machine cycle in a manner described hereinafter.

An irregular guide slot 263 (Fig. 2) is formed on the finger 259 and is guided over a rod 2 carried by a pair of spaced arms 2". The shape of the slot 263 is such that it coacts with the eccentric portion 26. of the sleeve 232 to cause the actuator finger 2", upon rotation of the shaft 26l, to enter between two of the teeth of gear 251 and thereafter advance thegear an increment of one tooth in a direction depending upon whether the machine is operated addition-' ally or subtractively. Near the completion of a cycle of operation of the machine the finger is returned to the position shown in Pig. 2 ready for the next actuation.

The arms 26! are journaled on bearing portions formed on the sleeve 262 concentric with the axis of rotation of shaft "I and are pivoted by means of pins 212' (Fig. 26) to arms 2" and 283', respectively, extending upwardly from the end plates HI and I32, respectively, of the shiftable transmission I03. Thus, the counting finger m is constrained to move with the shiftable transmission I03 and, whenever the tr is centralized in an operating position, the finger 259 is aligned with one of the gears 231.

The tens-transfer mechanism for the counter is similar to that employed for the accumulator described hereinbefore. This latter tranler mechanism comprises a plurality of transfer units mounted on a shaft 213 driven in timed relation with the counter drive shaft 2" in a manner described hereinafter. Each of the various transfer teeth, such as 2Ilv (Fig. 13), are similar to teeth 2|! and supported in a like manner, IO that they are adapted to be shifted longitudinally of the shaft 213 by a transfer lever 21. pivoted on a cross rod 2" supported by the various brace plates Ill. The transfer levers 2" are similar in construction to levers 2| and each is moved to transferring position by a transfer lever'politioning cam 23., secured to the hub 2 of the respective dial assembly (Fig 28) on movement of the respective counter dial "I from 9" to 0" during an additive rotation or from 0 to 9" during a subtractive rotation thereof. I

Since the counter mechanism comprises considerably fewer denominational orders than the accumulator mechanism, the various carry teeth 2" need not be arranged in a cross-over, staggered, relation as illustrated in Fig. 17. but may be arranged in any well known manner about the shaft 213, such as that disclosed in the United States patent to TalamlnL'No. 1,867,608. ilued July 19, 1932.

In order to indicate to the operator the particular denominational order of the counter mechwhichisflttedoverthesleeve menu-non lhinstendwieemevementrelativetotheeleen;

Arm 2" is guided intermediately along a cross rod 219 extending from one side to the other of thereof which is painted in a colo contrasting to that of the cover plate I11. The ear 219 is visible through one of a plurality of triangular openings the machine and has an ear 219 formed at the top I 219 (Figal and 2) formed in the cover plate 91 of the machine and disposed directly above the counter dials 2 9I.

Accumulator and counter clearing mechanism In order to. clear or reset the accumulator mechanism to zero, a zeroizing shaft 299 (Figs. 2, 14-and 18) is provided which is rotated by the hand crank I92 in a manner described hereinafter. Shaft 299 extends across the machine and has a plurality of mutilated gears 292 secured thereon, each adapted to mesh with one of the mutilated gears I92 of the different dial units. When the clear shaft 299 is in its normal full cycle position and the dialshells I99 stand at "0, the mutilated sections ofthe respective gears I92 and 292 will lie adjacent each other; Thus,-upon digimanner described hereinbefore, enabling the dial units, including their respective sun gears I99, to

be rotated by the gears 292, carrying with them the planet gears I92 and the gear carrier discs I99, without aflecting the gears I19. The shaft I99 supportingthe various pawls I91 and arms I I99 has secured to the right hand end thereof an arm 999 (Figs. and 18) which is pressed against the periphery of a notched disc 99I formed on a gear 992, forming part of the gear drive train for the clearance mechanism as will be described hereinafter. On movement of the gear train in any direction out of full cycle position,

rotation oLthe crank in one direction serving to clear the counter register dials and rotation in the opposite direction serving to clear the accumulator register dials.

Manually operated drive connections The entire calculating machine mechanism,

with the exception of the shift mechanism, is driven by a single hand crank I92 (Figs. 1 and 18). Crank I92. is secured to a shaft 994 journaled in bearings 999 and 999, the former being mounted in the end plate II9,,while the latter is mounted in an auxiliary supporting plate 991 spaced from the plate 9. The sh'aft 999 is slidable longitudinally in the bearings m and 999 and has a key 999 secured thereto and adapted to'be en ed in the keyway of either an actuator drive gear 999or a clearance drive gear 9I9, both of which are freely mounted side by side on the shaft 999 between the bearings 995 and 999. A

compression spring 9I I, moimted in a socket portion.9I2, forming part of the bearing 995 presses against the hub of the handle I92 to move the same to the right causing the key 999 to engage the gear 999, thus positioning the crank for normally operating the'actuating mechanism ofth'e machine. However. when both the clearance mechanism and the actuator mechanism are in full cycle position, the keyways formed in the gears 999 and 9I9 will be aligned with each oth'er, enabling the operator to press inwardly on the handle I92 and thus connect the shaft 994,

through the key 999, to the clearance drive gear train. After the handle I92 has been moved inwardly and thereafter slightly rotated in either direction, driving the'clearance mechanism, the

key 999 bears against the-left hand face of the gear 999 and prevents the spring 9I I from eturnthe disc "I will be rotated and the arm 999 will be rocked clockwise, causing the various arms- I I99 to be similarly rocked out of engagement with the pins II99 on pawls I91. As the gear train again reaches its'full cycle position, the arm 999 falls back into the notch on the disc 99I enablin the various planetary gear carrier discs I99 to be again locked for subsequent digitation.

The counter mechanism register, including the various dials 29 I, is cleared in a manner similar to that used in clearing the above mentioned accumulator register. For this purpo e, a counter clear shaft 299 extending across the machine is provided and has a plurality of mutilated gears 299, corresponding to those at 292, which are adapted to engage the corresponding mutilated gears 299 (Figs. 14 and 26) secured to the various counter dial units. Thus,'one complete rotation of shaft 299 will serve to clear th'e counter register.

' ing this driving means from the dial gear train of the counter.

Clearance of both the accumulator and counter register dials is accomplished by th'e hand crank Since the counter mechanism driving means com- 9 ing the shaft 999 to its normal rightmost position until a full cycle position of the hand crank I92, and consequently the clearance mechanism, is

reached.

Means (not shown) are preferably provided to insure a'complete revolution (one cycle of operation) of the hand crank I92 in any one direction before it is rotated in the opposite direction. For a disclosure of such means reference may be had to the above mentioned patent to Lerch, No. 7

With the addition of suitable clutches and controls, a motor (not shown) may be connected to the shaft 999 to effect a power drive. for the calculating machine mechanism.

9 Drive for accumulator and counter clearing mechanisms 9 Means are provided for operatively connecting the crank handle I92, when in driving engagement with the gear 9I9; to the counter clear shaft 299 when rotated in one direction and to the accumulator clear shaft 299 when rotated in the opposite direction. Thus, connecting the gear 992 (Figs. 18 and 23) to the drive gear 9I9 is an idler gear 9I9 journaled "on a bearing stud 9I9 secured to the end plate H9. The hereinbefore mentioned gear 992 is Journaled on a stud shaft 9I9 extending between the end plate I 9v m as will be described in detail hereinafter;

one end of which is ioumaled in a bearing 325 provided in the end plate H5. The other end of the shaft 324 is journaled in a bearing formed in a clutch member 333, which, in turn, is journaled in a bearing 33i provided in a plate 356. Secured to the clutch member 333 is a gear 335 entrained, through an idler 333, with a pinion 333 secured to the counter register clear shaft 295 which shaft is journaled in a bearing 332 supported by a plate 316 integrally secured to the plate 313.

The clutch member 3311 is adapted to be connected to the shaft 324 by a clutch arrangement generally designated at 331, the construction of which is disclosed and claimed in the above mentioned patent to Lerch, No. 1,927,269. Journaled on the shaft 32d, and also adapted to be connected thereto by means of the clutch arrange ment 331 is a gear 333 meshing with one of a pair of intermeshed idlers 339 and 333 journaled on shafts 321 and 325, respectively," independently of the idlers 322 and 321. The idler 346 meshes with a gear 34! secured to the accumulator register clear shaft 293.

The clutch arrangement 331 comprises (Figs.

18 to 22, inclusive) the clutch member 330, a second clutch member 345, a pair of clutch washers 348, one for each of the clutch members 333 and 345, and a compression spring 349 interposed between the two washers 348. The clutch member 345 has formed on the hub thereof (Fig. 22), a pair of diametrically opposed notches 346 which are engaged by corresponding projections on the gear 338, to secure these elements together. Each of the clutch members 330 and 345 has a flange formed thereon as at 338, in which are formed a pair of long and short depressions 351 and 352, respectively. Each of the washers 348 is provided with a tooth 353 (Figs. 20 and 21) which normally engages in the short depression of itsassociated flange 336, and is also provided with a camming projection 354 normally engaging the long depression of its associated flange. However, the tooth 353 on one of the washers 348 faces in a direction opposite to that of the tooth on the other washer. Both washers 348 are splined to the shaft 324 and are pressed into engagement with their respective clutch members by the compression spring 349. Thus, on rotation of the shaft 324 in one direction by the crank handle I02, one of the driving washers 348 will engage its respective clutch member to drive the same, while the other clutch member will be held out of engagement with its associated washer by virtue of the cam portion 354 on the washer, which slides on the full face of the flange and does not permit the tooth 353 to drop into engagement until a full revolution has'been completed.

Drive for actuating mechanism Meshing with the actuator drive gear 309 (Fig. 18) is a gear 351 secured on a drive shaft 358 (Figs. 18, 26, 32 and 33). This shaft is Journaled in bearings formed in end plates H5 and 360 and has mounted on the left hand side thereof a clutch 35!.

- The clutch 361 (Fig. 26A) is somewhat similar in construction to clutch 352, to be described in detail presently, and has a gear 363 secured to the driven side thereof, which is in mesh with a gear 364 (Fig. 26) secured to the driving side of clutch 332 mounted on the heretofore mencloned actuator shaft IN. The speed ratio between the gears 383 and 334 is one to two, so

that the main actuator shaft lOl, which is driven during the first portion only of each machine cycle, will complete a full rotation during one half revolution of the main start 358.

The clutch 361 is normally engaged when all of the multiplier keys 3B5 (Figs. 1 and 32) are in their raised position (during addition or subtraction operations) as will appear under the description of the multiplying mechanism.

Referring particularly to Figs. 30 and 31, the clutch 332 comprises a disc 333, the hub of which is Journaled on the actuator shaft 10L Disc 335 has a notch formed therein adapted to be engaged by a dog 361 pivoted on a pin 363 extending between the end plates of the clutch housing, one plate of which is pinned to the shaft m. The toothed end of the dog 361 is normally pressed into engagement with the disc 386 by a spring 383. The opposite end 351 or the dog 351 extends into an opening 310 formed on the periphery of the clutch housing and is adapted to be engaged by the toothed end 311 (Fig. 32) of a clutch operating dog 312 pivoted at 313 and urged in a counterclockwise direction by a tension spring 314.'

The gear 364 is riveted to the hub of disc 353 along with a second gear 313 which meshes with a gear 311 (Figs. 26, 32 and 34) of twice its diameter. Gear 311 is journaled on a stub shaft 314 extending from the end plate 330. A pin 332 extends from the side or the gear 311 and rides in an arcuate slot 381 provided in a cam disc I" which is also journaled on the shaft 313 independently or the gear 311. The cam disc 330 has a lobe 334 formed on the periphery thereof which is adapted to engage a roller 335 rotatably mounted on the upwardly extending end of the clutch operating dog 312 to rock this dog clockwise and therefor cause its tooth 3 to engage the clutch dog 331 (Figs. 30 and 31) and disen' sa e the clutch 332.

When the machine is in full cycle position, the

parts will be arranged as illustrated in Figs. 30

to 32, inclusive, with the pin 332 located 180 away from the point of contact 0! the roller 335 against the periphery of the disc 3", and with the clutch dog 351 in engagement with the notch in the clutch disc 358.

To centralize the main actuator shaft l0! in full cycle position a centralizer disc 500 (Figs. 32 and 33) is provided. This disc is pinned to the shaft HH and has a notch formed on the periphery thereof adapted to be engaged by a roller rotatably mounted on one end of an arm 302, which is pivoted at the other end on a pin 603 secured to a bracket "4, which is suitably secured to the under surface of the channel member 41. A spring 505 is tensioned between the arm 302 and 2. lug 505 extending from the channel member 41, to urge the roller 501 into engagement with the disc 800 and into the notch formed therein when the actuator shaft H is in full cycle position, or after it has been rotated through a complete revolution from full cycle position.

When the hand crank I42 (Figs. 1 and 18) is rotatedtrom full cycle position, the clutch 332 will transmit rotation to the actuator shaft, MI and thus effect a dlgltational entry into the accumulator. As the gear 311 (Figs. 32 and 34) begins to rotate. the pin 332 will move to one end or the other of the slot "I in disc 3", depending on the direction of rotation of the hand crank, and will then rotate the disc 334. At the end 0! the first half revolution of the hand crank I02, and consequently gear 311, the lobe 334 on disc 330 will 

